Ironing press



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IRONING PRES S Filed Nov. 2. 1932 5 Sheets-Sheet 3 W. M. EMERY :'UaoNINGf PRESS July 17, 1934.

Filed Nov. 2. 1932 5 Sheets-Sheet 4 INVENTOR.

W. M. EMERY IRONING PRESS July 17, 1934.

5 Sheets-Sheet 5 Filed NOV. 2. 1932 m. m n m .ir-illy l?, i934 IItfDNIN'G William M. Emery, Lansdowne, Pa. l Application November 2, i932, Serial No. 649,342

invention relates to improvements in ironnd pressing machines. Ironing presses in past have for the most part been designed commercial purposes in which highly speciald tresses are practical. In this invention I ve as an object the construction of one s, especially suited for domestic use, which .ifo .ld be as efficient for a large variety of work. as a group of specialized presses. For instance, in pressing a suit friction between the pressing elements is objectionable, but in ironing linens it very desirable; so I have had as an object ii this invention to provide means to produce :i ction between the elements and a uniiied selecl by women.

tive control means to allow or prevent said friction. Ii a press is to meet the requirements of the .iome it must .be suitable for ironing or press-y ooth fiat goods and fancy garments. The' machines previously designed either have had their pressing elements tapered or rounded at the ends to suit fancy garments or else have had square ends to facilitate flat ironing. An object of my invention is to provide a press with a shiftable buck, one end of which is especially adapted for the one tasl; and the other end suited for the other taslz.

In the domestic eld it is essential that the operating levers function as easily as possible at all points inasmuch as they are handled chieiiy In my invention I have purposed to accomplish this in four ways; first, by reducing to a minimum the vertical movements of the elements; second, by pre-setting the position of the elements according to Whether pressure only or iriction and pressure is desired by the operator; third, by utilizing the potential energy Aresident in the mass of the head at the time of the vertical drop to store forces to later actuate the substantially horizontal movement of one of the elements towards the other; and fourth, by providing new means to efciently balance the stroke of the operating lever so that the force required to operate it will tend to be substantially constant and uniform in all the positions and movements of the operating lever. Other purposes and objects will be apparent from the specification and claims `which follow.

li/Iany of the underlying principles of this invention are explained in great detail and are easily understood by reference to the following applications: application #570.518, application #581.540, application #606,096 and application #$13,469. All these applications should be considered as a unit forming a continuous development step by s step. An additional object is to bring the principles embodied in these earlier inventions to a further reiinement and fruition.

In the drawingsa Figure. 1 is an end view of a press embodying features of my invention with the actuating mechanism omitted,

Fig. 2 is an end view of a manual actuating mechanism suitable for the press shown in Fig. l.

Fig. 3 is a rear view of Fig. 2.

Fig. e is a front view of Figs. 1, 2 and 3, omitting certain rear parts better shown in Fig. 3, i. e. shaft 79, spring 81 and parts pertaining thereto,

Fig. 5 is a top View of the head and buck in various positions.

Fig. 6 is a larger scale View of the parts shown in Fig. l which function to produce friction between the elements.

Fig. 7 is a iront view of Fig. 6.

Fig. 8 is a section along line VIII- VIII in Fig. 6.

Fig. 9 is an end view of another form of press embodying features of my invention.

Fig. 10 is an end view of another form of press embodying features of my invention.

Fig. l1 is a larger scale view of the parts shown in Fig. 9 which function to produce friction between the elements, and,

Fig. 12 is a sketch showing the inolinationof the pressing head in random positions.

The position shown in unbroken lines is similar in all views. Numerals followed by a prime indicate a duplicate part or the left side of the machine. Numerals followed by an a indicate a slightly modied part in Figs. 9 to 11.

In the mechanism shown in the drawings such intangible features as a shifting center -of gravity, weights'of material, friction and the multiplicity of simultaneous movements, play an important part, therefore fine precision should not be expected in the drawings. Their accuracy is however, suicient to illustrate the mechanical principles involved and inasmuch as many modications are possible without departing from these principles and the spirit of this invention, the applicant feels that the interpretation of his invenion should not be limited to the structures herein as exemplified but rather to the mechanical principles set forth.

In Figs. 1 and 2 there is shown a rigid table top or base 15 to be suitably supported by legs or other means (not shown). This base 15 supports a resiliently and slidably mounted buck 16. Four supporting springs 17 rise from the base 15 to a plate 18. In the plate 18 are rigidly mounted four threaded sockets 19. Passing through the base 15, the center of the springs 17, and screwed into the sockets 19, there are four bolts which pre-stress the spring 17 to the proper tension to produce the desired pressure and resiliency, and to locate the buck at the desired height.

As shown in Fig. 5, there is formed, in the front and rear edges of plate 18, slots 21 in which four machine screws 22 slide. These screws are threaded into the buck, but are loose enough so that the buck may be slid sidewise for a limited distance such as 4 to 12 inches.

The buck 16 is of any construction customary in the art. One end indicated as 26 is rectangular in shape, while the other end 24 is tapered, rounded or angled to t fancy garments. A metallic pressing head 23, adapted to be heated, square at both ends, is mounted, as will later be described, to cooperate with the buck 16.

As shown in Fig. 5, when the buck is slid to a full extent in one direction, the rectangular` buck portion 26 cooperates with the whole rectangular working face of the head 23. In this position the elements are especially arranged to iron large flat pieces such as table cloths. The advantages of rectangular elements for performing progressive ironing operations is obvious. For instance, in ironing an average table cloth folded once 40 repetitional movementsof the presser head are required to cover the entire surface of the cloth. After each application of pressure the cloth is progressed the width of the rectangular area of the elements so that an edge of the head will register (if possible) with the portion previously pressed. With rectangular elements because of the parallel longitudinal sides this is simple, but with tapered or rounded elements it is necessary to overlap the impressions which greatly reduces the speed of ironing and results in uneven ironing and often scorching. However, for pressing irregularly cut garments rectangular elements are inconvenient. Because of the novel construction of my lower element my press provides the advantages vof both the tapered and the rectangular elements without their normally attendant disadvantages. When the buck is slid to the full extent in the other direction, the tapered or shaped end 24 is moved to cooperate with the head 23, especially adapting the machine for the ironing or pressing of shaped or fancy garments. The end of the buck out of use is very convenient for folding, arranging and supporting fabrics.

Without the cost or inconvenience of interchangeable bucks, the applicant has thus invented a way to adapt a single press to several types of work, a feature which the applicant believes to be new and valuable to the art.

Extending downwardly from the table or base l5 are two frames 25 and 25'. A rod 27 is journaled in and between these frames. Two identical mechanisms 28 and 28 as are shown in Figs. 6, 7 and 8 are fixed to rod 27 and function as will be later explained in connection with the frictional movements of the elements. These mechanisms consist of arms 30 and 30 directly attached by pins to rod 27. Midway of these arms there are bolts 31 and 31' which pivotally connect arms 30 and 30 with second arms 32 and 32 respectively. The pivotal movements between the arms 30 and 30' and 32 and 32 arerestricted by slots 33 and 33 in arms 32 and 32' and pins 34 and 34 in arms 30 and 30 respectively. A rod 35 is journaled in and between one end of the second arms 32 and 32.

To normally maintain these mechanisms extended, springs 36 and 36 are attached to extensions 37 and 37 from arms 32 and 32 and are stretched to anchorages 38 and 38' near rod 27 respectively. Two lock arms 39 and 39', journaled on rod 27, normally lock under gravity behind rod 35 and normally prevent rod 35 from approaching rod 27. An inner connecting rod 40 functions to cause the lock arms 39 and 39' to act as a unit.

Fixed to rod 35 is a large C shaped support arm 45, in the upper end of which is fixed a rod 46 which forms a pivotal connection with the presser head 23. This pivot is oiset slightly forward of the center of gravity of the presser head 23 so that the face of the presser head is not hung horizontally from support arm 45, but the front edge of the face is normally slightly raised. This is of great importance especially in pressesl utilizing a horizontal movement of one element to the other, because the head must be raised sufficiently above the buck not to muss the lay of the materials to be ironed. The inclining of the head accomplishes this with a vertical pressure movement of minimum length and thus the ultimate pressure is increased or the effort of operating is reduced. Also the pivotal mounting of the head is helpful in peeling ofi starched pieces which occasionally adhere to the head.

In order to determine the course, inclination, and position of support arm and accordingly head 23, a ball bearing roller 47 is mounted between two parallel extensions 48 and 48' from arm 45 for movement in a cam or guide track 49. The cam or guide track has a substantially vertical portion which gives to the presser head a vertical movement to and from the buck and it has an inclined portion which determines 'the substantially horizontal separation of the elements. The applicant uses the term horizontal in a most general sense and does not wish to infer that any particular part or parts of his device follow an exactly level or rectilinear course, for example see the forward movement of the head in Fig. 12.

The cam or guide track 49 is pivotally mounted at 50 to a support member 51 extending downwardly from and fixed to base 15. Integral with the cam or guide track is an arm 52 extending downwardly therefrom. The tip of arm 52 forms a cam 53'which is actuated by roller 54 mounted on a rod 55 extending between mechanisms 28 and 28. Rod 55 is journ'aled in extensions 56 and 56 from arms 30 and 30 respectively. The cam 53 is so arranged that about as soon as the presser head starts on its vertically downward course to the buck, roller 54 contacts with cam 53 and continues to turn cam 53, together with the guide track 49, clockwise about pivot 50, as viewed in Fig. 1, until the presser head approaches the limit of its movement, at which time cam 53 is shaped to produce no further result of movement. An arm 57 extends from the guide track 49 towards the front of the machine. A spring 58 normally held under compression by bolt 59 extends from the base 15 to said arm 57 and resists said clockwise turning of the cam or guide track 49.

When cam or guide track 49 has been turned by cam 53 and roller 54 to the limit of the movement thus further compressing spring 58, arm 57 is held from returning to its first position by a control catch 65, which normally hangs under gravity from a pivot 66 in such a position as to engage the end of arm 57. Pivot 66 is supported by arm 67 extending from support member 51, which is at- SCIl tached to base 15. Integral with the control catch is an actuating handle 68.

The means to actuate or turn shait 27 and thus operate the press is shown in Figs. 2 and 3, in which we see a cam lever arm 69 xedly mounted on shaft 27 between frames 25 and 25'. 1n this cam lever arm is seen a cam consisting of an arcuate portion 70 whose center is shaft 27 and another portion 71 which is at an angle to the arcuate portion 70. V

Operating in the cams of the cam lever arm 69 is a ball bearing roller 72 mounted in a radius arm 73 which is pivoted on rod 74 xed to frame 25. The manual operating lever 75 is attached to the radius arm 73.

Considering now only the portion 7l of the cam in the cam lever arm 69, it should be noted that the roller 72 is operating in this cam 71 at such times as a presser head is moving vertically towards or away from the buck. The position of the parts shown in the broken lines in Fig. 2 occurs when the head 23 is at the top of the vertical movement and is ready to descend. The position shown in full lines occurs when the full and nal pressure has been applied. This cam is so shaped that a slight movement of the operating handle at the position shown in broken lines will result in a relatively large movement of the head 23, whereas in the position shown in full lines a considerable movement of the manual level' is required to turn the cam lever arm 69 but slightly. Y

From the foregoing description, it would naturally be expected that, starting from the broken line position shown in Fig. 2 that considerable effort must be applied through the operating handle 75 to turn the guide cam track 49,y compressing spring 58, and also to apply the final pressure or action between the elements. From experience with other presses I have found this to be true and that the greatest effort is required towards the termination of this movement. Further it will be noted that when the operating handle 75 is moved counter clockwise as shown in Fig. 2 from the solid line position towards the position shown in broken lines that the work t0 be done is that of lifting the mass of head 23. Due to the leverage and the mechanical advantage, the initial part of this movement is practically eiortless leaving most of the work concentrated in the latter part as the position shown in broken lines is approached. However normally speaking by far the greatest effort is to be expected in producing the clockwise stroke.

One of the objects of this invention has been to overcome the lack of uniformity in the required work and effort so noticeable in other presses, and to distribute the work as evenly as possible throughout both strokes of the operating handle 75.

lThis is done with the aid of an extension arm 76 from the radius arm 73 forming therewith a bell-crank. A connecting link 77 connects extension arm 76 with a crank or radius arm 78, which is fixed to rod 79, journaled in and between frames 25 and 25. A torsional spring 81 of suincient length to produce practically uniform thrust is pre-stressed and wrapped about rod 79 and attached to crank or radius arm '78 and also to an anchorage member 80 fixed as to the base l5. Spring 8l urges the radius or crank arm 78 to turn counter clockwise (as shown in Fig. 2) in the direction of the arrow.

It will be noted that when the pressure is being applied, as shown in unbroken lines Fig. 2,' that the crank or radius arm 78 is in almost straight line dead center with the link 77-'giving to the torque forces of the prestressed spring 81 an amplied mechanical advantage resulting in forces which approach infinity tending to turn arm 76 the application of nalpressure by the operator. Likewise when the peak of the labor, as previously explained, occurs on the other stroke (the position shown in broken lines in Fig. 2), then crank or radius arm 78 is at right anglesto link 77, and more especially because extension arm 76 and link 77 are in a straight line dead center, the eiect of spring 81 upon the operating handle is completely nullied.

When the operating handle 75 is being turned counter clockwise as shown in Fig. 2 and the pressing head is being raised, energy is being stored in the torsional spring 81. This energy is stored much faster in the early part of this stroke than in the latter part, due to the relationship of the arm 78, extension 76 and connecting link 77. At the same time the work required to lift the mass of the head which may weigh 20 to 50 pounds is increased in the latter part of the stroke due to the eccentricities of the radius arm 73 and cam lever arm 69 and shape of cam 71. It should be noted that in the storing of potential energy chiefly first in one form then gradually changing until mostly in another form, one compensates with the other producing a uniform stroke during separation of the elements.

In'the same way that I have distributed the operating eiort, securing a surprising uniformity throughout the entire stroke, in Figs. 1 and 2, I have also distributed a little more of the work through the stroke easier for the operator, such as the counter clockwise stroke (because it is easier for an operator when seated to push down on a lever than to pull up) in the modified forms shown in Figs. 9 and 11; the modification being in the strength or pre-stressing of spring 81 accordingly is not showable in the drawings.

1n the operation of my press beginning with the position shown in full lines in Fig. 1, if we depress operating lever 75 (Fig. 2), then the head will .be raised and at the same time energy will be stored in the torsional spring 81. As soon as roller 47 reaches the top of the vertical portion of the cam or guide track 49, the head moves away in a substantially horizontal direction from the buck under gravity. (The cam or guide track 49 being at this time in a position to produce this movement.) During this gravity movement, roller 72 is idling in portion 70 of the cam lever arm 69.

Early in the construction of a press embodying these principles it is necessary to ascertain the general position of the center of gravity of theA head and support arm 45 and moving parts attached thereto. However the theoretical center of gravity shifts somewhat due to the varied positions of the parts pivotally attached to arm 45. This can best be ascertained empirically and compensated for in the nal adjustments. In the drawings, such as Fig. 1, the position of the center of gravity is assumed to be at the point indicated by C.G. and to travel along the adjacent dot dash line.

From this it will be noted that the cam or guide` track 49 is so shaped that in conjunction with the rest of the construction such as the pivots at rods 27 and 35, the center of gravity will gradually drop as the gravity movement progresses and clockwise and thus greatly facilitates or increases finally that it levelsout at the end of each stroke to slow up the movement.

When the operator desires the head 23 to come forward again, he presses a control handle 68 away from him releasing arm 57, which thereupon turns counter clockwise (Fig. 1) under the force of spring 58. This tips the cam or guide track 49 and raises the center of gravity (see dot dash line Fig. l) whereupon the presser head comes forward under gravity. When the presser head attains such a position that the roller 47 reaches the vertical portion of the cam or guide track 49, roller 72 is in the cam portion 71 of the cam lever arm 69, and a clockwise movement of the operating lever 75 Fig. 2 will cause the head to descend. Simultaneously roller 54 contacts with cam 53 and turns the cam or guide track 49 clockwise until the track reaches its final position where it is held in place by control catch 65. It is obvious that, according to the severity of the angle of the cam 53, the mass of the head may be sufficient to energize the initial part of the gravity drop. Fig. 1 shows such a construction and Fig. 10 shows a construction where cam 53 has a severe angle that would prevent the mass of the head from initiating the vertical movement without the aid of force applied through operating handle 75.

In such instances where the operator desires pressure only without friction between the elements, the operator completes the clockwise movement of the handle 75. Torsional spring 8l eases the required work to effectuate the final part of this movement.

It is important that the frame be as rigid as possible and that the height of the buck be accurately set if it is desired not to waste work by unnecessarily compressing springs 17. The general height of the buck may be set by means of bolts 20 to provide for full pressure without noticeable flex of the springs under normal conditions.

In such instances as the operator desires to produce friction as well as pressure between the elements, it will be noted from the intermediate broken line position shown in Fig. 1 that the buck must be in a higher position to contact with the head earlier than is necessary when pressure only is used. To provide for this adjustability of the height of the buck to suit the conditions for the use of friction, a plate 85 is set under the head of the bolts 22 and two ears 86 and 86' are bent upward from said plate. In these ears is journaled a rod 87. Two ears 88 and 88 are bent downward from the base l5 and between them is journaled eccentrically a rod 89. Two connecting links 90 and 90 interconnect rod 87 and eccentrically journaled rod 90. An operating control handle 91 is xed to the eccentrically journaled rod 90. Attached to handle 91 is an obstructing arm 92. When the handle 91 is depressed springs 17 extend themselves raising the buck slightly; and the obstructing arm 92 is moved into position to obstruct the downward movement of locking arms 39 and 39 and unlatch them.

When the parts are in the position just described, the operator moves handle 75 up or clockwise. With the aid of energy stored in the mass of the shoe and with the aid of energy stored in torsional spring 81 and further work done by the operator, the cam or guide track 49 is turned clockwise as before mentioned and the head is lowered until it contacts with the buck in its high position as shown in broken lines in Fig. l.

As the movement of the operating lever 75 is continued, second arm 32 pivots on bolt 3l in arm 30 and spring 36 is extended. Thus the shaft 35 is drawn closer to shaft 27 and the roller 47 acts as a fulcrum and the pressing head is pushed forward on buck 16 producing friction therebetween.

When the press of Fig. l is arranged as just described to apply friction as well as pressure, partly on account of the fact that the buck 16 is resiliently supported by springs 17 and that the frictional movement is incidental to the pressure and not positively actuated and because of the resultant of forces which actuate the frictional movement fbecome less as the movement progresses, a valuable characteristic is noticeable, i. e. that the frictional movement is a deferred or retarded movement. The springs 17 are compressed simultaneously with the application of pressure storing energy therein. The frictional movement tends to relieve this spring compression and exhausts some of this stored energy and continues and completes the frictional movement somewhat after the pressure has been fully applied. This is desirable because the frictional movement is thereby prolonged in time while the fabrics are being subjected to pressure. There being friction between the elements resisting the sliding movement of one element on the other, it is important to properly balance or proportion actuating forces with the retarding forces. This arrangement also facilitates the actuation of the press. A press with members arranged and proportioned substantially as shown in Fig. l will be found to possess these characteristics.

As shown only in Fig. l it will be seen that roller 47 is slightly ahead (in the direction of the line of travel of the head when applying friction) of a line dropped perpendicularly to the face of the buck from the pivotal connection between the head 23 and the support arm 45. This forward position may be exaggerated at will according to the :zo-efficient of friction between the buck and the head until it is enough to materially facilitate the frictional movement.

When sufficient heat and pressure has been applied by the head 23 the operator moves the operating handle 75 counter clockwise (Fig. 2) and the head is moved back across the face of the buck for additional friction by springs 36 and 36. Because of the now lower position of cam or guide track 49, the presser head 23 commences its horizontal backward movement at a point lower than the point at which the vertical drop of the head was initiated. By the time the mechanisms 28 and 28' are raised or turned to this point the roller 72 is in cam portion 70 ready for the gravity movement to commence and the locking arms 39 and 39 have again assumed their locking positions between shafts 27 and 35.

It should be noted in connection with the frictional sliding of the elements that the stationary element i. e. the buck, is of longer dimensions, front to back, than the head so that none of the area of the head will be uncovered or not in use when the frictional movement is functioning. If the elements, i. e. the head 23 and the buck 16, were of the same dimensions front to back and were lined up when pressure only was applied. then their effective surface would be reduced probably ten percent when one was slid on the other. The applicants invention avoids this condition and speeds up the ironing accordingly.

In Fig. 9 is shown one of the modified forms of my invention; the head is suspended pivotally from its ends by two arms 45a. The mechanism 28 and 28 are called 28a and are reversed to move the head rearwardly on the buck instead of forward as in Fig. 1.

Fig. 11 shows this construction. 'I'he parts are similarly numbered to those in Fig. 6 except for the addition ofletter a. Mechanism 28a which interconnects rods 27 and 35 is composed of a radius arm 30a which is pivotally attached to radius arm 32a by the hex bolt 31a. In one end of the bell crank 32a is a slot 33a through which a loose bolt'34a passes to limit the pivotal movement between the two arms 30a and 32a. Journaled into the other end of the bell-crank second arm is rod 35. Extending from an anchorage on radius arm 30a near rod 27 to an anchorage on the bell-crank second arm 32a near rod 35 is a spring 36a which is prestressed and tends to draw the rods 27 and 35 together. A single locking arm 39a to prevent, at certain times, a departing of the arms 30a and 32a from their normal positions is mounted to pivot on rod 27 and to engage the far side of rod 35.

The means to raise and lower the buck when pressure only instead of friction and pressure is desired is eliminated from this modified construction shown in Fig. 9. It is replaced with the following construction: To each end of a horizontal shaft 102, suspended from base 15,

-is aixed hook 103 and midway of said shaft 102 is fixed another hook 104. The supporting bearings of shaft 102 are tight enough to cause hooks 103 and 104 to remain in any position in which they are set. Pivotally attached to the bottom of the buck is a catch member ,105 to cooperate with hook 104. It hangs under gravity and is so shaped that it may swing counter-clockwise but cannot swing clockwise from its normal position shown in Fig. 9. The lower hook 103, when it is turned clockwise to the position shown in broken lines in Fig. 9, engages locking arm 39a causing its withdrawal from Contact with rod 35, thus permitting the frictional movement.

When pressure only is desired control handle 106 is pushed in and the operating handle 75 is actuated. The rst time the pressure is applied the springs 17 are compressed but hook 104 engages catch member 105 and prevents the buck from rising when the pressure is released.

Later when the operator changes to a new type of ironing and desires friction as well as pressure he pulls control handle 106 towards him which disengages the buck to permit it to rise to the proper position for frictional ironing and simultaneously with the movement of control handle 106, hook 103 moves into a position to engage locking arm 39a at the proper instant to permit the frictional movement.

In Fig. 9 certain parts are not shown such as the cam or guide track 49. The working of the parts not shown are similar to those shown in Figs. 1, 2, 3 or 10.

In Fig. 10 is shown another modification of my press. It differs from Fig. 1 in that the mechanism 28 is reversed as in Fig. 9 and that the means for selecting the desired movement, that is pressure only or friction and pressure is vested in the buck support.

. The buck is supported by four radius arms 112 piv'otally mounted on rods 110 journaled in ears 113 turned up in the base 15 and pivotally attached to ears turned down from a plate 114 -on which the buck is slidably mounted as previously described. One of the four radius arms has a bell-crank portion 115 which furnishes an anchorage for a spring 116 which is attached to the base 15 by a hook 117. Also the bell-crank portion 115 furnishes a pivotal connectionfor a U shaped strap 120 which hangs always vertically under gravity.

When the buck is in the forward position it is locked there by a control bolt 119 which passes through the U shaped strap 120, which strap, because of its loose pivotal mounting and the bevel end of bolt 119, will hook itself around the bolt should the bolt be' moved to the position shown when the radius arms are in the position shown in broken lines.

In Fig. 10 it will be noted that the positions of the radius arms shown (the normal starting position in full lines and the normal extended position in broken lines) are equally inclined from the vertical and their movement being relatively short, the buck is mounted for a substantially horizontal movement, although the position may be varied by varying the starting position. However should something unusually thick be placed between the head 23 and the buck 16 the head will contact while there is yet considerable movement left before the turning of shaft 27 has been completed. In this case assuming that the U shaped strap 120 is not locked by the control bolt 119 the buck will be drawn further back than the position shown in broken lines. However as soon as the broken line position is passed the buck drops with increasing rapidity and soon automatically adjusts itself for the added thickness being pressed. l

Note should be taken that when such an extreme position is required the bell-crank portion 115 tends to assume a right angle relationship with spring 116 and thus increases the effectiveness of the spring and balances any tendency for the radius arm 112 to turn under the vertical pressure from the head rather than the lateral movement of the head.

The movement of the buck from the position shown in solid lines in Fig. 10 to the position shown in broken lines by reason of the horizontal moveros ment of the head is eifectuated by toggle 28a aided by the frictional engagement between the head and the buck, despite the action of spring 116 and any slight elevation of the buck due to the arcuate movement o'f the pivots supporting it.

In operation the head 23 always moves backwards at the termination of each pressure movement and forward at the initiation of the release of the pressure. When pressure only is desired the buck 16 is left free to move with the head and when friction is desired the buck is locked in position by the control 119 so that the head must slide on the buck or on the material being ironed. In Fig. 10 as well as such as construction in Fig. 9, the cam or guide track 49 is actuated by a radius arm, separate and distinct` from mechanism 28a, fixed midway of the shaft 27 in which is mounted a roller 54a which operably` contacts cam 53 of arm 52.

The applicant has not felt it necessary to show or describe means to motorize the presses shown in the drawings as such means is identical to that shown in my copending application #606.096,

In the claims the term congurative potential energy is used. It may be defined as potential energy resulting from the distortion or temporary change of shape of resilient bodies. For example, the compression of spring 58 (Fig. l) when the cam or guide track 49 is turned clockwise on pivot 50 from the position shown in broken lines to the buck constituting,

position shown in solid lines. The term positional potential energy may be defined as potential energy resulting from the raising or lifting of an object or anything possessing weight and accordingly subject to gravitation. For example, positional potential energy is stored in the moving parts of my press when, by the tipping of the guide track 49 counter-clockwise (Fig. l) from the solid line position to the position shown in broken lines by forces due to configurative potential energy resident in spring 58, the center of gravity of the moving parts is raised or lifted from the extreme right hand end of the approximate path of the center of gravity shown in dot dash lines (Fig. 1) to the highest point of said path.

I claim:

1. In a press, a head and a buck constituting pressing elements, a movable support arm for the head, means to support and actuate said support arm operably connected thereto below said head; a pivotal point of oscillation for said support arm, means to oscillate said arm to cause friction between the elements and means to raise and lower said arm to apply pressure between the elements.

2. In a pressing machine, two pressing elements, means to move one element to the other and means to apply friction and pressure therebetween when one element is held substantially stationary, control means to release the last mentioned element to move in the direction of said previously mentioned application of friction as a unit with the first mentioned element after pressure is applied, thus eliminating said friction but maintaining said pressure.

3. In a press, a head and a buck constituting pressing elements, a supporting arm for the head, guide track means and radius means toV support and actuate said head, said radius means including a rst arm member attached to an actuating shaft and second arm member pivotally attached to said supporting arm and means to pivotally interconnect the first and second arm members, resilient means to resist pivotal movement between said rst and second arm members, means to translate the pivotal movement between the rst and second arm members to effectuate a frictional movement between the elements and means to prevent the pivotal movement between the first and second arm members at the direction of the operator.

4. In a press, a head and a buck constituting pressing elements, support means to move the head to the buck, said movement being only in part substantially vertical, means to translate the positional potential energy in the head and its support means during the said vertical movement of the head to the buck into configurative potential energy to effectuate a substantial part of the rest of the movement of the head to the buck.

5. In a press the combination of a head and a when cooperating, substantially horizontal pressing elements, a support arm for the head means to swing the support arm to move the head laterally above the face of the buck and thereafter downwardly into pressing engagement and pivotal means to hang the head from said support arm with the face of the head normally slightly inclined in relationship to the buck to provide a greater clarance between the approaching edges of the elements as the head moves over the buck previously to the application of pressure.

6. In a press, a rectangular head having parallel longitudinal sides and small radius Corners so that an imprint of the head may register with the next adjoining imprint without overlaps or gaps in progressively pressing flat fabrics, a buck longer than said head, said buck having a rectangular portion of a size and shape to correspond with said head for pressing fiat goods and also a portion reduced in size for pressing garments and means to enable the buck to be shifted to place either of said portions into position of register with the head.

7. In a press, pressing elements including a rectangular head and a buck longer than said head, part of which is rectangular and part of which is rounded or tapered in the horizontal cross section, means to apply pressure between the head and the buck and means to enable the operator to shift the buck to place the different portions of the buck in engagement with the head.

8. In a press, a head Yand a buck, constituting pressing elements, means to effectuate relative movement of approach and separation of said elements, means to apply final pressure between said elements, an operating lever mounted for a back and forth movement to actuate said means, and means to distribute the work to actuate said lever between its two movements, the work required to actuate the movement of separation being substantially uniformly distributed during one stroke of said lever.

9. In a press, a head and a buck, constituting pressing elements, means to move one of said elements t0 apply pressure and friction between the elements and a single means operable at the discretion of the operator to prevent the application of said friction and to slightly raise the buck.

10. In a press, a head and a buck constituting pressing elements at least one of which is substantially horizontal, means supplying general support for and effecting bodily movement of one of said elements towards and away from the other, means to apply vpressure to effectuate a sliding movement of one element against the other 'actuated by the first mentioned means through a substantially horizontal movement of 120 the point of attachment between the movable element and the first mentioned means and means located below the'pressing elements having operative connection with said first mentioned means to actuate said means thereby effectuating 125 the application of pressure and the said sliding movement of one element against the other.

11. In a pressing machine for fabrics, two pressing elements, means for bodily moving one of said elements relative to the other, means to 130 store congurative potential energy in the moving means during the movement of one of said elements to the other and to convert said stored energy into positional potential energy in the movable element, and control means to effect said conversion when the elements are separated so as to enable said movable pressing element to move under the force of gravity towards the other element.

12. In a press, a head and a buck constituting pressing elements, means to move one of said elements towards and away from the other and apply pressure between them, a radius arm, operative connections between said radius arm and the first mentioned means, a spring prestressed 145 to tend to turn said radius arm to facilitate the application of pressure and means to transmit forces independently of the said radius arm and spring to actuate the first mentioned means.

13. In a press, a head and a buck constituting 150 pressing elements, means to move the head to ply pressure and friction against the buck and a single control means operable both to prevent the application of said friction and to vary the height of the buck.

'141. in a press, a head and a buck. constituting pressing elements, means to mount the head for movement to the buck forcing the head against the buck, means to frictionally slide the head across the buck While the elements are pressed together, control means to render said last mentioned means inoperative and means to automatically vary the height of the buck simultaneously with the movement of said control means to effect substantially the same pressure between the elements independent of the operativeness or inoperativeness of the means to slide the head frictionally.

15. in a press, a head and a buck constituting pressing elements, means to move one of said elements to the other applying pressure therebetween, means to normally move one of said elements substantially horizontally While said elements are in contact, means to mount the other element for movement twith the movable element only during the said horizontal movement and control means to, at the will of the operator, render said other element immovable, requiring the movable element to slide against the other element to complete its movement.

16. In a press, a. buck and a head constituting cooperable pressing elements, a supporting frame for the buck, means to mount the head in said frame for a compound movement including a short movement of the head, said short movement applying and relieving pressure between the elements and a longer movement of the head angular to the short movement completely uncovering the buck, means to substantially balance the forces acting on the head during the longer movement thus permitting the actuation of the longer movement with a minimum exertion of force, means to actuate the'frst mentioned means including a pivotally mounted cam arm member and a roller member mounted in a radius arm member co-acting therewith and means to exert force on one of said members to effectuate the entire movement of the rst mentioned means.

WILLIAM M. EMERY.

A its 

